Speed control for spinning machines and the like



Jan. 2, 1962 J. R. LONG 3,015,204

SPEED CONTROL FOR SPINNING MACHINES AND THE LIKE Filed Dec. 22, 1959 4Sheets-Sheet 1 O W LO m lNvEN ToR: JOHN E. LONG gg wwm h ATTORNEYS SPEEDCONTROL FOR SPINNING MACHINES AND THE LIKE Filed Dec. 22, 1959 J. R.LONG Jan. 2, 1962 4 Sheets-Sheet 2 IN VENTOR.

ATTORNEYS JOHN R. LONG Jan. 2, 1962 J. R. LONG 3,015,204

SPEED CONTROL FOR SPINNING MACHINES AND THE LIKE Filed Dec. 22, 1959 4Sheets-$heet 3 INVENTOR. JOHN R. LONG ATTORNEYS Jan. 2, 1962 J. R. LONGSPEED CONTROL FOR SPINNING MACHINES AND THE LIKE Filed Dec 22, 1959 4Sheets-Sheet 4 COMPRESSOR 2 Wrap INVENTOR JOHN 2. LONG ATTORNEYSPatented Jan. 2, 1962 ice 3,tl15,204 SPEED (IQNTRGL FOR SPINNINGMAEHINES AND TEE LIKE John R. Long, Hickory, N.C., assignor to Shut'ordMills, Inc, Hickory, N.C., a corporation of North Carolina Filed Dec.22, 1959, Ser. No. 851,318 22 tClaims. ((33. 57-98) This inventionrelates to an improved apparatus for controlling the, speed of spinningmachines, twisting niachines and other winding machines charac erized byrings movable with a traversing ring rail for winding yarn on yarncarriers, such as bobbins, spools and the like. The present invention isdisclosed in association with a spinning machine, although it is to beunderstood that the present invention may readily be adapted to othertypes of textile winding machines.

This application is a continuation-in-part of my copending applicationentitled Variable Speed Control for Winding Machines, Serial No.635,346, filed January 22, 1957, now Patent No. 2,918,779.

The distance between the usual ring-traveler of a spinning machine, orthe like, and the bobbin, when initial turns of yarn are being woundthereon, is much greater than it is when a relatively large number ofturns of yarn have been wound on the bobbin. Thus, in machines which aredriven at a constant speed, there is a much greater drag placed on theyarn by the traveler when only a few turns of yarn are wound on thebobbins, as compared to the drag on the yarn when a substantial numberof turns of yarn have been wound on the bobbins. Accordingly, the yarnis relatively taut as it is initially being wound on the bobbin and thetautness of the yarn gradually diminishes as the diameter of the packageincreases. For this reason, the speed with which the usual spinningmachine could be operated had to be limited in order to avoid placingextensive tension on the yarn during the initial winding of the yarn onthe bobbin.

in order to facilitate faster operation of such machines, various meanshave been provided for progressively increasing the speed of the machinewith increases in the diameter of the yarn wound on the bobbins thereof.

One type of apparatus used for progressively increasing the speed of themachines is disclosed in my United States Patent No. 2,803,107 grantedAugust 20, 1957, and wherein the speed of the machine is increased eachtime the ring rail moves in one direction only, with each reciprocationthereof, by increasing the amount of pressure directed into afluid-pressure-operated expansible or variable speed pulley which drivesthe machine.

My said copending application discloses and claims apparatus forregulating the speed of the spindles and the ring rail, with meansresponsive to movement of said ring rail in one direction for opening avalve interposed in a pressure line to a variable speed pulley of thecharacter described, and means responsive to movement of the rail in theopposite direction for closing the valve. Generally, the direction offlow of pressure is reversed in the valve controlling the variable speedpulley disclosed in said copending application, each time the ring railstarts to move upwardly or downwardly with each reciprocation of thering rail or builder motion. While this has been satisfactory in manyrespects, it has been found desirable to vary the time which theincreased and decreased pressure in the variable speed drive isinitiated, in each instance, relative to the operation of the buildermotion and ring rail, so the variable speed drive is more efficient inchanging the speed of the machine precisely at the instant desired.

It is therefore an object of this invention to provide an improvedapparatus for controlling a fluid-pressure-operated variable speed drivefor a spinning machine or the like, which apparatus includes means forincreasing and decreasing the speed of the machine predetermined amountsat predetermined intervals relative to respective movements of areciprocating ring rail in opposite directions.

For example, in forming a filling wind, the present apparatus producesgradual increases and decreases in machine speed relative to apreconceived optimum speed. A gradual increase in speed is initiatedimmediately before the ring rail starts each downward stroke, and agradual decrease in machine speed is initiated immediately before thering rail starts each upward stroke. The changes in speed are initiatedby effecting corresponding changes in the direction of flow of fluidpressure to the variable speed drive, and may be eiiected within anyreasonable ran e of variation during each movement of the ring rail ineach direction.

The variable speed drive of the present invention includes a variablespeed pulley provided with relatively movable cones or flanges aboutwhich a tensioned V-belt' is entrained, with fluid pressure means formoving the cones toward each other. The V-belt is also entrained about apulley fixed on the main shaft of the machine and separates said coneswhen fluid pressure is released from the variable speed pulley. Variablespeed pulleys of this type are disclosed in my United States Patent Nos.2,810,296 and 2,877,528. From the foregoing, it is apparent that thevariable speed pulley must move, as a unit, relative to the fixed pulleyand in direct relation to changes in the relative positions of the conesso the belt is properly tensioned at all times.

It is therefore another object of this invention to provide afluid-pressure-operated support for said variable speed pulley, whereinfluid pressure is applied to said support in predetermined proportion tothe discharge or release of pressure from the cones of said variablespeed pulley, so as to move the support away from the fixed pulley andthus tighten the belt and separate the cones. Conversely, as pressureincreases in the variable speed pulley and moves the cones thereoftoward each other, pressure is proportionally released from said supportso the belt may readily pull the support toward the fixed pulley as theeffective diameter of the variable speed pulley is increased.

Some of the objects of the invention having been stated, other objectswill appear as the description proceeds when taken in connection withthe accompanying drawings, in which FIGURE 1 is a side elevation of aspinning machine, omitting the creel, and showing my improved variablespeed control in association therewith;

FIGURE 2 is an enlarged fragmentary view looking at the opposite side ofthe machine from that shown in FIGURE 1, but omitting the centralportion thereof;

FIGURE 3 is a fragmentary sectional plan view, partially in section,showing the variable speed drive mechanism in the left-hand portion ofFIGURE 2;

FIGURE 4 is a somewhat schematic vertical sectional View showing thebuilder motion and parts of the improved control mechanism and beingtaken substantially along line 44 of FIGURE 2;

FIGURE 5 is a fragmentary vertical sectional view taken along line 5-5in FIGURE 4;

FIGURE 6 is a transverse vertical sectional view taken substantiallyalong line 6-6 in FIGURE. 2;

FIGURE 7 is an enlarged longitudinal vertical sectional view through oneof the regulator valves taken substantially along line 77 in FIGURE 3;

FIGURE 8 is a longitudinal vertical sectional view through the variablespeed pulley shown in the lower lefthand portion of FIGURE 2;

FIGURE 9 is a schematic diagram of the improved variable speed controlapparatus.

Referring more specifically to the drawings, the machine shown comprisesdrafting rolls 10 (FIGURE 1) supported on roll stands 11 fixed to a beam12 spaced above a spindle rail 13 at each side of the machine. Oppositeends of beams 12 and spindle rails 13 are supported on head-end andfoot-end frame members 14, 15. A main cylinder shaft 16 is journaled inframe members 14, and has a cylinder 17 thereon which drives belts ortapes 2%. Tapes 20 impart rotation to spindles 21 at opposite sides ofthe machine. Spindles 21 are supported by spindle rails 13 and havecorresponding yarn carriers, bobbins or spools 22 mounted thereon, abouteach of which yarn Y is wound to form a yarn package 23.

The machine includes a yarn traversing means embodied in a verticallyreciprocable ring rail 24, mounted on each side thereof, which supportsa plurality of rings 25. Rings 25 encircle yarn packages 23. Each ring25 has a traveler 26 thereon for guiding yarn from drafting rolls 10onto the corresponding bobbin or spool 22.

In its course from drafting rolls 16 to the bobbins 22, each strand ofyarn Y passes through a guide 27 so the yarn balloons as it passesthrough a corresponding traveler 26 and inwardly to the correspondingbobbin 22.

Main cylinder shaft 16 drives drafting rolls 10, through conventionalmechanism enclosed in the head-end frame member 14, and also drives abuilder motion for reciprocating ring rail 24. The builder motion isbest shown in FIGURE 4, this builder motion being of a conventional typeused for building a filling-wound package. That is, with each cycle ofthe machine, ring rails 24, rings 25 and travelers 26 commence directingyarns to the bobbins while in a relatively low position and the lengthof each vertical stroke thereof is substantially the same throughoutformation of the packages 23.

However, ring rails 24 are progressively stepped upwardly so that, witheach upward movement of each ring rail 24, the diameter of the packagegradually increases. Conversely, with each downward stroke of each ringrail 24, the diameter of the packages gradually increases and,ultimately, the upper end of each package of yarn is taperedsubstantially as shown in FIGURES 1 and 2. The lower portions of bobbins22 may be tapered so the lower end of each filled package 23 isstraight.

The filling-wind builder motion, broadly designated at 30, may be of atype which includes a cam 31 driven to rotate continuously byconventional means, not shown, connected with main shaft 16. Theperiphery of cam 31 is engaged by a builder follower 32 projecting froma main builder lever 33 pivotally mounted, as at 34, on head-end framemember 14.

A rack 35, carried by lever 33, also has a roller or rack follower 36thereon which engages a curved upper surface on an auxiliary builderlever or builder arm 44 also pivotally supported at 34. Rack is shifted,in a step-bystep manner, to gradually change the range of movement ofarm 40, although the length of each stroke of the free end of arm 40 mayremain substantially constant, all of which is well known in the art.

The end of main builder lever 33 remote from rack 35 is usually providedwith a weight 41 to assist in main taining follower 32 in engagementwith the lower surface of cam 31. The curved upper surface on arm 40 ismaintained in engagement with follower 36 by the weight of ring rails 24and intervening parts. Such intervening parts may include a chain orpliable element 4-3, one end of which is connected to the free orforward end of builder arm 40. Pliable element 43 extends upwardly,passes over a suitable guide means 44 carried by the headend framemember 14, and then extends to an arm 45 (FIGURE 1) whose lower end isfixed on a rocker shaft 46 journaled in brackets depending from spindlerails 13.

Rocker shaft 46 also has a litter arm or lever 56 thereon beneath eachof the spindle rails 13. One end of each lifter arm has a follower orroller 51 thereon upon which rests the lower end of a correspondinglifter rod 52. A plurality of said lifter rods 52 is provided at eachside of the machine, although a single lifter rod 52 is shown inFIGURE 1. Lifter rods 52 are guided for vertical movement in thecorresponding spindle rails 13 and support, at their upper ends, thering rails 24.

Each lifter arm 51 is provided with a weight 53 which normally urges thecorresponding ring rail 24 upwardly, as is conventional, and therebymaintains the curved upper surface (FIGURE 4) of builder arm 40 inengagement with follower 36.

Since builder motion 3%? and other parts of the machine heretoforedescribed are conventional, a further detailed description thereof isdeemed unnecessary. It is with a machine substantially of the characterthus far described that the present invention is parti ularly adapted tobe associated.

It is a well known practice to drive spinning machines and the like bymeans of an electric motor, such as the motor indicated at 66 in FIGURES1, 2 and 3. However, the electric motor 6tl is mounted in the mannershown in the present drawings so as to be moved away from the main shaft16 of the machine under fluid pressure and to be moved toward the mainshaft 16 with respective decreases and increases in the effectivediameter of a variable speed pulley assembly 61, the changes ineflective diameter of the pulley assembly 61 being controlled byapparatus peculiar to the present invention.

Motor 66 is preferably of the constant speed type and the variable speedpulley assembly 61, mounted on the driven shaft 62 of motor 611, may beof a type such as is disclosed in either of my said United StatesPatents Nos. 2,810,296 and 2,877,528. Pulley assembly 61 may be mountedon either shaft 62 or 16 without departing from the spirit of theinvention. The fluid-pressureoperated motor support may be ofsubstantially the type disclosed in my copending United Statesapplication Serial No. 639,769, filed February 12, 1957, now Patent No.2,927,471 and entitled Belt Tensioning Motor Support.

The pressure exerted upon the support for electric motor 60 and variablespeed pulley assembly 61 is substantially inversely proportional to thefluid pressure applied to the variable speed pulley assembly 61. This isan important novel feature of the present invention, since it providesfor smooth and eflicient changes in the speed of the machine and insuresproper tensioning of the belt engaging the cones of pulley assembly 61.

It will be observed in FIGURES 1, 2 and 3, that main shaft 16 has a\l-pulley 63 fixed thereon, which may be termed as a fixed pulley.V-pulley 63 is engaged by at least one endless V-belt 64 which is alsomounted on pulley assembly 61. Pulley assembly 61 (FIGURE 8) is apreferred embodiment of pneumatic or fluid pressure actuated means forregulating the speed of spindles 21, ring rails 24, rolls 10 and othermoving parts of the machine.

Pulley assembly 61 comprises a pair of relatively movable cones orflanges 65, 66. Both cones 65, 66 may move relative to a sleeve 67 onwhich they are mounted, as disclosed in said United States Patent No.2,810,296, or only one of the flanges, such as flange 66 in thisinstance, may move relative to said sleeve 67 as disclosed in saidUnited States Patent No. 2,877,528. In this instance, sleeve 67 is keyedto motor shaft 62, as at '71 and is also secured against axial movementon shaft 62 as by means of a set screw 71.

Cone 66 has a tubular hub 72 keyed, as at 73, on sleeve 67. Stationarycone or flange 65 is keyed on hub 72, as at 74, so as to permit movableflange 66 and its hub 72 to move axially of stationary flange 65 whilepreventing relative rotational movement between flanges- 65, 66. Theouter end of hub '72 is secured to the inner wall of a hollow cylinder'75.

A piston 76 is disposed within cylinder 75 and a flexible diaphragm 77is preferably secured between the outer Wall and annular side wall ofcylinder 75. Piston 76 is provided with a plurality of inwardlyprojecting pins 89 thereon which loosely penetrate said inner wall ofcylinder 75 and bear against the outer surface of stationary flange 65.The outer end wall of cylinder 75 has a tube 82 journaled therein, as bymeans of anti-friction bearing 83. Tube 82 establishes communicationbetween 21 pipe or conduit 84- and the interior of cylinder 75; betweendiaphragm 77 and the outer end wall of cylinder 75.

The variable speed pulley assembly 51 is shown in FIGURE 8 as though allfluid pressure had been released from the cylinder 75 thereof, in whichinstance, tensioned V-belt 64 will have moved movable flange 66 awayfrom flange 65 so the pulley assembly 61 transmits relatively slow speedrotation to fixed pulley (:3 and, consequently, to the machine. It willbe noted that piston 76 has a hub 35' integral with or suitably securedthereto, which hub is secured in the outer end of inner sleeve 67 as byscrews 86. Accordingly, when compressed air or fluid pressure isintroduced into cylinder 75 through tube 32, diaphragm 77 pressesagainst piston 76, and fluid pressure is likewise applied against theinnor surface of outer wall of cylinder 75.

It is apparent that this moves cylinder 75 from left to right oroutwardly in FIGURE 8. In so doing, piston 75 pulls hub 72 and movableflange 6:6 therewith, to move flange 66 toward flange and thus increasethe effective diameter of variable speed pulley assembly 61. It isapparent that the motor 64 must move toward fixed pulley 63 in orderthat the bi ht of belt 64 may move radially outwardly relative toflanges 65, 66. 7

As heretofore stated, electric motor 60 is preferably of the constantspeed type, and it will be noted that electric motor tit may beenergized by means of a pair of electrical conductors 90, 91 (FIGURE 1)having a plug or electrical connector 92 on the free ends thereof whichmay be connected to a suitable source of electrical energy, not shown.Conductor 91 may have a manually operable switch )3 interposed thereinfor controlling the flow of current to electric motor 60.

Electric motor 60 is fixed upon a movable support or slide 95 guided ina base 96 suitably secured to the floor F upon which the machine rests.One end of support 5 has the movable part 100 of a fluid motor orfluidpressure-operated ram assembly 97 suitably connected thereto. Inthis instance, ram assembly 97 is shown in the form of a cylinder andpiston arrangement, the movable part thereof being shown in the form ofa piston rod, and the stationary or fixed part being shown in the formof a cylinder 101.

Piston rod llll) slidably penetrates the head-end of cylinder 101 andhas a suitable piston 102 fixed on the inner end thereof and which ismounted for axial sliding movement in cylinder 191.

The end of cylinder 1111 opopsite from piston rod 100 is closed and hasone end of a conduit 1% communicatively connected thereto. As best shownin FIGURES 6 and 9, the ends of conduits 84, 103 remote from variablespeed pulley assembly 61 and ram $7 are connected to corresponding sidesof respective pressure control valve means or regulator valves broadlydesignated at 155, MP6, to the other side of which compressed air orfluid pressure may be introduced by respective conduits 107, 1&8connected to a suitable source of pressure or compressed air 111, as bymeans of a branch conduit 112. Conduits 84, 103 are preferably providedwith respective pressure indicating gauges G. Conduit 112 may also beprovided with a suitable manual operable shut-off valve 113 interposedtherein.

Pressure regulator valves 1tl5, 1116 may be identical and, thereforeonly regulator valve will be described in detail and like parts of bothvalves 1%, 106 shall bear the same reference numerals where applicable.Various types of regulator valves may be used for controlling the flowof fluid pressure to variable speed pulley assembly 61 and ram assembly97, just so long as each valve is capable of gradually changing pressurebetween predetermined minimum and maximum pressures in the cylinder 75of variable speed pulley assembly 61 and cylinder 101 of ram 97 withrespective outward and inward movements of respective operating plungersthereof.

Pressure regulator valve 105 is shown, in FIGURE 7, in the form of ahousing comprising an upper or primary part 115 and a lower or secondarypart 116 having a flexible diaphragm 119 fixed therebetween. Axiallyopposed primary and secondary valve plungers 117, 118 are mounted forrelative coaxial movement in the valve housing, both valve plungers 117,118 being of hollow construction.

Valve plunger 11% is also of built-up construction and is fixed to thecentral portion of diaphragm 119. One end of a relatively heavyregulator spring 121 bears against the secondary valve plunger 11%. Thepressure of spring 121 against valve plunger 11% and diaphragm 119 ismanually determined by means of an adjustment or regulator screw 122.The housing part 115 of regulator valve has a sleeve or tubular guide123 fixed therein in which the upper or primary valve plunger 117 ismounted for longitudinal sliding movement. Valve plunger 117 is reducedat its upper or outer end and loosely penetrates the restrictedcorresponding end of sleeve 123, thus forming a shoulder on the uppervalve plunger 117 for limiting upward movement thereof.

A compression spring 124- normally urges the shoulder on upper plunger117 against the restricted upper end of sleeve 123. The end of spring124 opposite from upper plunger 117 is seated against the correspondingend of lower or inner plunger 118. The upper end of plunger 118 is loosein sleeve 123 so that air may pass therebetween.

Plungers 117, 118 are provided with respective valve seats 12 againstwhich respective interconnected valve members c, d are adapted to beseated. A compression spring 125, within upper plunger 117, normallyurges valve member c against its seat a. The housing part 115 ofpressure regulator valve 105 has a pair of passageways e, f thereinwhich communicate with the respective conduits 1tt7, 84 and extendthrough sleeve 123 at opposite sides of an enlarged medial portion orpiston g on upper valve plunger 117.

Upper valve plunger 117 has one or more passageways h for establishingcommunication between passageway e and valve seat a. The portion ofvalve plunger 1.17 below the piston g has one or more passageways jtherein, establishing communication between passageway and the interioror lower portion of upper valve plunger 117. The lower housing part 116has an opening 126 therein which communicates with the atmosphere. Thelower end of the inner or lower plunger 118 also has openings k thereinwhich communicate with lower housing part 116.

In order that the manner in which variation of pressure in cylinder 75of variable speed pulley assembly 61 is effected may be clearlyunderstood, a description of the manner of operation of pressureregulator valve will now be given.

The movable parts in both pressure regulator valves 105, 1% normallyoccupy the position in. which the parts of pressure regulator valve 195are shown in FIGURE 7 under minimum pressure conditions; that is, attimes when a minimum amount of pressure is present in the respectivecylinders 75, 101. It is apparent that regulator screw 122 (FIGURE 7)determines the amount of pressure exerted by spring 121 againstdiaphragm 119 and inner plunger 118. Thus, adjustment screw 22determines either the maximum or min mum pressure which may enter thecylinder '75 of pulley assembly 61 or the cylinder ltll of ram assembly97, as the case may be.

In this instance, the flanges 65, 66 of pulley assembly 61 are shown inmaximum opened or separated position so the pulley formed therefrom isof a minimum effective diameter. Flanges 65, 66 are moved toward eachother by moving the upper plunger 117 of regulator valve 105 downwardlyrelative to upper housing part to gradually open pressure regulatorvalve 115 in accordance with the rate at which plunger 117 thereof ismoved downwardly.

As plunger 117 and its piston g move downwardly in FIGURE 7, lower valved bears against seat b on lower valve plunger 118, so that valve seat 4moves away from upper valve member with further movement of the uppervalve plunger 117. This movement of valve seat a away from upper valvemember 0 permits compressed air to flow from the source 111, throughconduits 112, 107 and passageway e into sleeve 123. Thus, fluid pressureor compressed air flows through passageway h in the reduced medialportion of upper plnuger 117, past valve seat a, through passageway 1',through passageway 1, through conduit 34 and tube 82 into cylinder 75.it is apparent that this causes flange 66 to move toward flange 65.

In the event that line pressure is greater than th amount of pressuredesired to be admitted to cylinder 75 to obtain the desired maximumspeed of the machine; that is, to obtain the desired maximum effectivediameter of pulley assembly 61, regulator screw 122. of regulator valveHi5 may be so adjusted that, upon a predetermined amount of pressurebeing present in the cylinder 75, and consequently, in the lower portionof sleeve 123, the pressure present in the lower portion of the sleeve123 may then be such, relative to the pressure exerted by the regulatorspring 121 as to move lower valve plunger 118 away from the lower valvemember d and permit excess pressure to escape from the pressureregulator valve Ill-5. The minimum pressure to be maintained in cylinder75 is determined by the extent to which plunger 117 is permitted to moveupwardly toward closed position.

From the foregoing, it is apparent that regulator valve 1% functions inthe same manner as regulator valve N5 in determining the maximum andminimum range of pressure in cylinder 161 of ram assembly 97 whenregulator valve 1% is closed and opened by lowering and raising plunger117 of regulator valve 1196.

Referring again to FIGURE 7, when pressure is to be released fromcylinder 75 of pulley assembly 61, plunger 117 is permitted to moveupwardly, under pressure of spring 124, to substantially close valveassembly M5. In so doing, seat a of upper plunger 117 engages uppervalve member 0, thus moving lower valve member d away from seat b onlower plunger 118. This permits air to escape from the lower portion ofsleeve 123 in accordance with the rate at which plunger H7 is permittedto move upwardly. Of course, lower plunger 118 also moves upwardly asthe pressure escapes past valve seat b to the extent effected byregulator spring 121. It follows that, if lower plunger 11% stops upwardmovement before valve 1; has reached its maximum upward movement, thenthere will be no positive pressure in the cylinder 75. However, if theregulator screw has been so adjusted that lower valve (1 ceases to moveupwardly prior to lower plunger 118 having reached the limits of itsupward stroke, a predetermined minimum pressure will remain in cylinder75.

As heretofore stated, the pressure in cylinder 101 of ram assembly 97 issubstantially inversely proportional to the pressure in cylinder 75 ofvariable speed pulley assembly 61. Thus, whenever the effective diameterof the pulley 65, 66 is increased by the admission of pressure intocylinder 75, belt 64 rides toward the outer peripheral surfaces offlanges 65, 66 and a proportional amount of pressure is released fromcylinder 101 of ram 97 so that belt 6 need not overcome excess pressurein cylinder till, in order to move motor 60 and support toward fixedpulley s3 and main shaft 16, when the effective diameter of pulley 61 isincreased.

Conversely, when pressure is released from cylinder 75, pressure isproportionally increased in cylinder 101 to move motor as and itssupport 95 away from fixed pulley 63 and main shaft 16 to produce anoptimum amount of additional tension in belt 65 such as to move flanges65, be apart from each other the desired distance to produce apredetermined minimum speed of the machine.

in order to produce the desired changes in the eifective diameter of thepulley assembly 61, at predetermined ranges, relative to verticalreciprocation of ring rails 24, and to also produce the inverselyproportional changes in pressure in cylinders 75, lull of pulleyassembly 61 and ram assembly @7, I have provided a novel apparatus forgradually closing regulator valve N5, as valve 1% is gradually opened,and vice-versa, and which means operates in timed relation to theoperation of the spinning machine.

To this end, I have provided an operating lever which is pivotallymounted intermediate its ends, as at 131, on foot-end frame member 15 inspaced relation above regulator valves 1525, 1%. Regulator valves 105,196 are suitably secured to frame member 15 below operating lever 130 asbest shown in FIGURE 6. Valves 165, 1% may be mounted for verticaladjustment on frame member 15 so they may be located in proper relationto operating lever 13%.

Operating lever 136 is provided with a pair of adjustable abutments 132,133 which may be spaced substantially equal distances from oppositesides of pivot point 131. Abutments 132, 133 are shown in the form ofadjustment screws or set screws threaded through operating lever 1349and being locked in adjusted position by respective lock nuts 134. Thelower ends of screws 132, 133 may be so arranged as to engage theplungers 117 of respective regula or valves 1&5, res. However, since theplungers and the screws are relatively small, an intermediatetransmission or equalizing lever 135 is positioned between abutments132, 133 and the plungers 117 of regulator valves M5, 106. It will benoted that equalizer lever 135 is also pivotally mounted intermediateits ends, as at 136, on frame member 15, and diametrically opposedportions thereof bear against the upper ends of plungers 117.

Operating lever 133 has one end of a pliable element or sprocket chainpivotally connected thereto, as at 141. Pliable element Mil extendsupwardly from lever 134i, passes over a sprocket wheel 142 journaled onone of the spindle rails 13 (FIGURE 4), then extends substantiallyparallel with the corresponding spindle rail 13, and then passesdownwardly over another sprocket wheel 14?; suitably journaled on thelatter spindle rail 13.

The end of pliable element 14-0 opposite from lever 130 is pivotallyconnected, as at 144, to the outer end of a follower arm or controllever 145 which is oscillatably mounted intermediate its ends, as at146, on the headend frame member lid. Pivot point 146 is preferablyclosely adjacent the end of lever 145 to which pliable element Mt) isconnected. The end of follower arm 145 opposite from sprocket chain 1 inhas a cam follower or anticipator 147 mounted for longitudinaladjustment thereon, and being urged into engagement with the peripheryof builder cam 31, as by means of a tension spring 150 (FIGURES 2, 6 and9).

One end of tension spring 159 is connected to the end of actuating lever13%, to which pliable element 140 is connected, and the other end oftension spring 150 is connected to foot-end frame member 15. in orderthat follower 147 may be adjusted longitudinally of follower lever 145,it will be observed in FIGURES 4 and 5 that lever 145 is provided with alongitudinally extending ad- 3,01 secs 9 justment slot 151 thereinthrough which a reduced threaded portion of a shoulder bolt 152 extends.Follower 147 is in the form of a roller rotatably mounted upon the bodyof shoulder bolt 152.

The reduced portion of shoulder bolt 152 is provided with nut 153 whichmay be loosened for adjusting bolt 152 and follower 147 longitudinallyof slot 151, and which nut 153 may then be tightened to secure thefollower 147 in the desired adjusted position. The position of the speedcontrol or anticipator follower 147, relative to builder motion follower32 and cam 31, determines the instant at which changes in speed commencerelative to the position of ring rails 24.

it will be noted that builder cam 31 is substantially symmetrical and,since a short period of time is required for the eifective transmissionof pressure changes between the regulator valves 1&5, 1% and therespective cylinders i5, 101, it has been found desirable to reverse thedirection of flow of fluid pressure or compressed air through regulatorvalves 165, 1156 slightly in advance of the initiation of each reversalin direction of movement of the ring rail as it reaches respectiveuppermost and lowermost positions during the course of reciprocationthereof. The reversal of air flow in regulator valves 105, 166 inadvance of the reversal in direction of movement of ring rails 24 isdesirable in order that the changes from increasing to decreasing speedand decreasing to increasing speed of the machine are effectivesubstantially simultaneously with the changes in direction of movementof the ring rails 24 to thereby prevent a sudden slackening or excessivetensioning of the yarn between the travelers 26 and the yarn carriers2.2 or packages 23. Thus, it will be observed in FIGURES 4 and 9 thatfollower 147 is located in advance of follower 32 relative to the highand low surfaces of cam 31.

As shown in FlGURES 4 and 9, builder follower 32 is positioned at thehighest point (the point of largest radius) of one of the lobes ofbuilder cam 31, at which point the ring rails 24 would occupy theirhighest position in the winding of a particular layer of yarn onto thepackage. The ring rails 24 are shown in FIGURES 1 and 2 as being in alowered position for purposes of clarity. The high point of the lobe ofcam 31 opposite from follower 32 has moved beyond anticipator follower 1.7 so that the flow of compressed air into cylinder 75 of variable speedpulley assembly 61 has already been initiated, sulhciently in advance ofthe start of the next downward movement of ring rail 24, in order toinsure that the pulley flange 66 starts to move toward pulley flange 65by the time the ring rails 24 actually start their next downwardmovement.

Of course, as heretofore stated, as regulator valve 165 starts to close,for introducing pressure into cylinder 75 of variable Speed pulleyassembly 61, regulator valve 106 starts to open to exhaust fluidpressure or compressed air from cylinder 131, so that belt 6 2- may pullmotor 61) and support 95 toward fixed pulley 63 as the effectivediameter of the variable speed pulley assembly 61 is increased.

it will be noted that, as cam 31 rotates in the direction indicated(FIGURE 4), anticipator earn 147 moves downwardly toward the nextsucceeding lower surface of builder cam 31 and builder follower 32approaches the next succeeding low surface of cam 31. Spring 1541 lowerstherewith the left-hand portion of actuating lever 13% and abutment 132bears against and lowers the corresponding end of intermediate lever135. In so doing, the left-hand portion of lever 135 moves downwardlythereby depressing plunger 117 of regulator valve 1115 to gradually openregulator valve 1535 and thereby gradually introduce compressed air orfluid pressure into cylinder '75 (FIGURES 8 and 9) of variable speedpulley assembly 61.

At the same time, abutment 133 moves upwardly or away from theright-hand portion of intermediate lever 135, which, in turn, is movedupwardly by plunger 117 of regulator valve 105, thus gradually closingregulator valve so that pressure is gradually released from cylinder161. Prior to the succeeding low surface of cam 31 approaching builderfollower 32, which is immediately prior to ring rails 24 reachinglowermost position, anticipator follower 147 is engaged by the nextsucceeding lowermost surface of builder cam 31 so that the left-hand endof actuating lever 13!) then starts to move upwardly immediatelypreceding initiation of the next succeeding upward stroke of ring rails24.

It follows that upward movement of the left-hand portion of actuatinglever 131 (FIGURE 9) moves abutment 132 away from, and abutment 133toward, respective portions of intermediate lever 135 which portions, inturn, to permit plunger 117 of regulator valve to gradually moveupwardly as plunger 117 of regulator valve 1% gradually movesdownwardly. Accordingly, regulator valve N5 is gradually opened asregulator valve 1% is gradually closed. Thus, pressure is graduallyreleased from cylinder 75 of variable speed pulley assembly 61 as it isgradually increased in cylinder ltll of ram assembly 97.

Thus, pulley assembly 61 is gradually moved away from fixed pulley 63under predetermined and sufiicient pressure to cause belt 64 togradually increase the distance between cones or flanges 65, 66, thusgradually decreasing the effective diameter of pulley assembly 61 andgradually decreasing the speed or" the machine.

As heretofore stated, the adjustment screw 122 on each regulator valveM5, 106 may be adjusted downwardly relative to lower housing part 116 soas to permit a predetermined maximum pressure to flow through the valveto the respective cylinders when plungers 117 are fully depressed oropened, or screws 122 may be adjusted upwardly relative to lower housingpart 116 to permit a predetermined minimum pressure to continue to flowthrough the respective valves to the respective cylinders when theplungers 117 are in fully raised or closed position.

During operation of the machine as thus far described, the screws 122are preferably adjusted for the minimum pressure desired to bemaintained in the cylinders 75, 101. Obviously, the minimum and maximumpressures which should be introduced into the cylinders 75, 1'91 dependsupon many variables including the sizes of the cylinders, the desiredspeeds of the machine and the chartacter of the yarns being wound onpackages 23 In one application of this apparatus, in running onethirtiesto one-nineties cotton strands, it was found desirable to vary thepressure in the ram assembly cylinder 1431 from a minimum of ten poundsper square inch to a maximum of twenty pounds per square inch, whilemaintaining the pressure in the cylinder 75 of the Variable speed pulleyassembly at from a minimum or twenty pounds per square men to a maximumof forty pounds per square inch.

If it is desired to increase or decrease the amount of minimum pressurewhich maybe present in cylinders 75, 191 when the plungers 117 of therespective regulator valves 13S, llld are in raised or substantiallyclosed position, the adjustment screws 132, 133 are adjusted downwardlytoward bar 135 relative to actuating lever 13%. Conversely, if it isdesired that the minimum pressure present in the cylinders 75, 1191 isdecreased when the pningcrs .117 are in fully raised position, thescrews 132, 133 are adjusted upwardly relative to bar 135 in theactuating lever 13%. Of course, the maximum pressure which may beintroduced into cylinders 3'5, ltll when the respective plungers 117 aremoved downwardly is determined by adjustment of the lower regulatorscrews 122 on respective valves 195', 195.

In the event that regulator screws 122 cannot be adjusted to produce thedesired range of variation in pressure, the valves 1%, 106 may bevertically adjusted, since their housings are preferably provided withslots S 11 through which their holding screws H extend (FIGURES 6 and7).

If it is desired that the machine is operated at a constantpredetermined speed, screws 132, 133 may be a"- justed upwardly relativeto or removed from actuating bar 13%, thus rendering the gradual speedmechanism inoperative, and the regulator screws 122 may be adjustedupwardly to move each respective valve member (FEGURE 7) ofi of its seata so that a predetermined constant pressure will enter and pass througheach valve 195, 1%. Of course, when said predetermined pressure ispresent in the sleeve 123 of each regulator valve, with an excesspressure therein, the diaphragm 119 and lower plunger 118 movedownwardly slightly to permit excess pressure to escape between thevalve d and valve seat b.

Referring to FIGURE 9, it will be noted that adjustment of anticipatorfollower 147 on follower lever i4 determines the instant each inversechange in machine speed is effected, without necessarily changing therate,

range or extent of speed variation effected by the cam 31,

by the screws 132, 133 (or location of valves ms, 21%), and by theregulator screws 122, respectively. The rate of speed variation is thefrequency at which relative changes in machine speed occur. The range ofspeed variation is the distance the ring rail may move during eachgradual increase and each gradual decrease in machine speed. The extentof speed variation is the difference between (1) the speed of themachine at the start of each inverse change in machine speed and (2) thespeed of the machine at the end of each such change in machine speed.

It is thus seen that I have provided a novel apparatus for controllingthe speed of a spinning or similar machine in which the changes in thespeed from decreasing to increasing, or vice-versa, may be eil'ected atany time independently of vertical reciprocation of the ring rail 2 andwherein the range and extent of the gradually increasing and graduallydecreasing speeds may be accurately predetermined independently of theinstants (or locations of the ring rail) at which inverse changes inspeed are initiated. It is seen further that I have provided meanswhereby increased pressure is applied to the motor 69 and its variablespeed pulley assembly 61, away from the fixed pulley 63, whenever theeffective diameter of the variable speed pulley assembly is decreasedand, conversely, wherein the pressure is proportionally released fromthe motor 60 and Variable speed pulley assembly 61 in accordance withincreases in the effective diameter of the variable speed pulleyassembly 61.

In the drawings and specification there has been set forth a preferredembodiment of the invention and, although specific terms are employed,they are used in a generic and descriptive sense only and not forpurposes of limitation, the scope of the invention being defined in theclaims.

I claim:

1. A textile machine having spindles and at least one ring rail, meansfor driving said spindles and continuously reciprocating said rail,fiuid-pressure-operated means for regulating the speed of the spindlesand the ring rail, a valve adapted to produce variation of pressure insaid fiuid-pressure-operated means, means controlling the rate, rangeand extent of pressure variation produced by said valve, meansautomatically operable at a predetermined interval relative toinitiation of each movement of said rail in one direction for openingsaid valve and being antomatically operable at a predetermined intervalrelative to initiation of movement of said rail in the oppositedirection to close said valve, and means for adjusting saidautomatically operable means independently of said controlling meanswhereby the intervals at which the opening and closing of said valveoccur may be determined independently of the rate, range and extent ofspeed variation effected by said valve and independently of the locationof the ring rail.

2. A textile machine having spindles and at least one ring rail, meansfor driving said spindles and for continuously reciprocating said rail,pneumatically actuated means for regulating the speed of the spindlesand the ring rail, a valve adapted to produce variation of pres sure insaid pneumatically actuated means, means controlling the rate, range andextent of pressure variation produced by said valve, means automaticallyoperable a relatively short interval before initiation of each movementof said rail in one direction for opening said valve and beingautomatically operable a relatively short interval before initiation ofmovement of said rail in the opposite direction to close said valve, andmeans for adjusting said automatically operable means independently ofsaid controlling means whereby the intervals at which the opening andclosing or" said valve occur may be de termined independently of therate, range and extent of speed variation effected by said valve andindependently of the location of the ring rail.

3. A textile machine having spindles and at least one ring rail, meansfor driving said spindles and reciprocating said rail, pneumaticallyactuated means for regulating the speed of the spindles and the rail,valve means adapted to produce variation of pressure in saidpneumatically actuated means, means automatically operable prior totermination of movement of said ring rail in one direction forinitiating the opening of said valve means and for gradually openingsaid valve means during subsequent movement of said rail in the oppositedirection, and said automatically operable means being operable toinitiate closing of said valve means immediately prior to termination ofmovement of said rail in said opposite direction and to gradually closesaid valve means during subsequent movement of said rail in said onedirection.

4. A textile machine having spindles, at least one ring rail, a buildermotion having a reciprocatory arm coupled to said rail for reciprocatingsaid rail, means for driving said builder motion and said spindles,means responsive to fluid pressure to regulate the speed of said motionand said rail, a valve adapted to produce variation of pressure at saidpressure-responsive means, movable means on said valve for controllingthe same, means operatively associated with said reciprocatory arm forproducing an increase in pressure in said pressureresponsive means withmovement of said reciprocatory arm in one direction and for eifectimreduction in pressure in said pressure-responsive means with movement ofsaid reciprocatory arm in the opposite direction, and said operativelyassociated means being operable to initiate each increase and eachreduction in pressure, in each instance, immediately prior to saidreciprocatory arm reaching the terminus of each movement of said arm insaid opposite direction and in said one direction respectively.

5. A structure according to claim 4 wherein said valve is provided withmeans independent of said movable means for governing the maximumpressure admittable to said pressure-responsive means.

6. In a machine having means for traversing yarn onto a rotating yarncarrier in a reciprocatory manner while maintaining the strokes of thetraversing means substantially constant and progressively advancing thetraversing means in one direction to form a filling-wound package on thecarrier; the combination therewith of fluid-pressureoperated means forregulating the speed or" the yarn carrier and the traversing means,valve means adapted to produce pressure variation in saidfluid-pressure-operated means, means controlling the rate, range andextent of pressure variation produced by said valve means, meansautomatically operable at a predetermined relatively short intervalpreceding initiation of movement of said traversing means in onedirection for opening said valve means, said automatically operablemeans being operable a predetermined interval preceding initiation ofmovement of said traversing means in the opposite direction to closesaid valve means, and means for adjusting said automatically operablemeans independently of said controlling means whereby the intervals atwhich the opening and closing of said valve occur may be determinedindependently of the rate, range and extent of speed variation effectedby said valve and independently of t.-e location of said traversingmeans.

7. A textile machine having spindles and at least one ring rail, meansfor drivin the spindles and reciprocating the rail, pneumaticallyactuated means for regulating the speed of the spindles and the ringrail, a first valve adapted to produce variation in pressure in saidpneumatically actuated means, means operable automatically apredetermined interval preceding cach movement of said ring rail in onedirection for initiating the opening of said valve and for graduallyopening said valve during the subsequent movement of said ring rail insaid one direction, said automatically operable means also beingoperable to initiate the closing of said valve a predetermined intervalpreceding movement of said ring rail in the opposite direction and togradually close the valve during said movement of the rail in saidopposite direction, and means for adjusting said automatically operablemeans for determining the intervals in which the opening and closing ofsaid valve is initiated relative to said movements of said ring rail inone direction and in the opposite direction, respectively.

8. In a machine having means for traversing yarn onto a rotating yarncarrier in a reciprocatory manner While maintaining the strokes of thetransversing means substantially constant and progressively advancingthe traversing means in one direction to form a filling-Wound package onthe carrier; the combination therewith of fluid-pressureoperated meansfor regulating the speed of the yarn carrier and the traversing means,valve means adapted to produce a variation of pressure in saidfluid-pressureoperated means, means automatically operable apredetermined interval preceding each movement of said traversing meansin one direction for initiating opening of said valve means and forgradually opening said valve means during subsequent movement of saidtraversing means in said one direction, and said automatically operablemeans being operable to initiate the closing of said valve means apredetermined interval preceding initiation of movement of saidtraversing means in the opposite direction and for gradually closingsaid valve means during subsequent movement of said traversing means insaid opposite direction.

9. A spinning machine having spindles and a reciprocating ring rail, amain shaft adapted to rotate said spindles and to reciprocate said rail,a driven shaft disposed adjacent said main shaft, a first pulley fixedon one of said shafts, a fluid-pressure-operated expansible pulleymounted on the other of said shafts, at least one V-belt entrained oversaid pulleys, a conduit extending from a source of fluid pressure tosaid fluid-pressure-operated expansible pulley, means operativelyassociated With said ring rail for at least initiating an increase inthe amount of pressure directed into the fiuid-prcssure-operatedexpansible pulley at a predetermined interval preceding the initiationof movement of said ring rail in one direction, saidoperativelyassociated means being operable to at least initiate a decrease in theamount of pressure directed to the fluid-pressure-operated expansiblepulley immediately preceding the initiation of movement of said ringrail in the opposite direction, and said expansible pulley being soarranged that increased pressure correspondingly changes the effectivediameter of the expansible pulley and decreased pressure inverselychanges the effective diameter of the expansible pulley to therebyeffect corresponding changes in the speed of the machine.

10. A spinning machine having spindles and a reciprocating ring rail, amain shaft adapted to rotate said spindles and reciprocate said ringrail, a driven shaft disposed adjacent said main shaft, a first pulleyfixed on one of said shafts, a fiuid-pressure-operated expansible pulleymounted on the other of said shafts, at least one V-belt entrained oversaid pulley, conduit means extending from a source of fluid pressure tosaid expansible pulley, a pressure regulator valve interposed in saidconduit means, means for at least partially opening said pressureregulator valve to correspondingly increase the amount of pressuredirected into the expansible pulley immediately prior to each movementof said ring rail in one direction with reciprocation thereof, saidlast-named means also being operable for at least partially closing saidpressure regulator valve to correspondingly decrease the amount ofpressure directed into the expansible pulley immediately prior tomovement of said ring rail in the opposite direction With eachreciprocation thereof, and said expansible pulley being so arranged thatincreased pressure increases the effective diameter of the pulley anddecreased pressure decreases the elfective diameter of the pulley andthereby respectively increases and decreases the speed of the machine.

11. A spinning machine having spindles and a reciprocating ring rail, amain shaft adapted to rotate said spindles and to reciprocate said rail,a driven shaft disposed adjacent said main shaft, a first pulley fixedon one of said shafts, a fluid-pressure-operated expansible pulleymounted on the other of said shafts, at least one V-belt entrained oversaid pulleys, a conduit extending from a source of fluid pressure tosaid fiuid-pressure-operated expansible pulley, means automaticallyoperable at a predetermined instant prior to each movement of said ringrail in one direction for initiating an increase in the amount ofpressure directed into the fluid-pressure-operated expansible pulley andfor gradually increasing the amount of pressure directed into thefluid-pressure-open ated expansible pulley during the subsequentmovement of said ring rail in said one direction, said automaticallyoperable means also being operable to initiate a decrease the amount ofpressure directed into the fluid-pressureoperated expansible pulley at apredetermined instant preceding each movement of said ring rail in theopposite direction for gradually decreasing the amount of pressuredirected to the fluid-pressure-omrated expansible pulley duringsubsequent movement of said ring rail in said opposite direction, andsaid expansible pulley being so arranged that increased pressurecorrespondingly changes the effective diameter of the expansible pulleyand decreased pressure inversely changes the effective diameter of theexpansible pulley to thereby efiect corresponding changes in the speedof the machine.

12. A spinning machine having spindles and a reciprocating ring rail, amain shaft adapted to rotate said spindles and to reciprocate said rail,a driven shaft disposed adjacent said main shaft, a pulley mounted oneach of said shafts, one of said pulleys being a fluid-pressureoperatedexpansible pulley, at least one V-belt entrained over said pulleys, amovable support for said driven shaft, means for increasing the amountof pressure diected into the expansible pulley With movement of saidring rail in one direction, said means being operable for decreasing theamount of pressure directed into the expansible pulley with movement ofsaid ring rail in the opposite direction, said expansible pulley beingso arranged that increased pressure corrmpondingly changes the effectivediameter of the expansible pulley and the decreased pressure inverselychanges the effective diameter of the expansible pulley to therebyeffect the corresponding changes in the speed of the machine, and meansautomatically operable for yieldably moving said support and itscorrespondiru pulley in a direction away from the other pulley when theeffective diameter of the expansible pulley is decreased, and means forreleasing said lastnamed means so the l-belt pulls said support and itscorrespondin pulley toward the other pulley when the diameter of theexpansible pulley is relatively increased.

13. A spinning machine having spindles and a reciprocating ring rail, amain shaft adapted to rotate said spindies and to reciprocate said rail,a driven shaft disposed adjacent said main shaft, a pulley mounted oneach of said shafts, one of said pulleys being a fluid-pressure-operatedexpansible pulley, at least one ll-belt entrained over said pulleys, amovable support for said driven shaft, means for gradually increasingthe amount of pressure directed into the expansible pulley with movementof said ring rail in one direction, said means being operable forgradually decreasing the amount of pressure directed into the expansiblepulley with movement of said ring rail in the opposite direction, saidexpansible pulley being so arranged that increased pressurecorrespondingly changes the effective diameter of the expansible pulleyand the decreased pressure inversely changes the effective diameter ofthe eXpansible pulley to thereby effect the corresponding changes in thespeed of the machine, means automatically operable for moving saidsupport and its corresponding pulley in a direction away from the otherpulley under gradually increasing yieldable pressure when the effectivediameter of the expansible pulley is decreased, and means for graduallyreleasing the pressure applied by said last-named means so the V-beltpulls said support and its corresponding pulley toward the other pulleywhen the diameter of the expansible pulley is relatively increased.

14. In a variable speed drive for a spinning machine and the like havinga pair of spaced substantially parallel shafts, one shaft being driven,a pulley on each shaft, an endless belt entrained over said pulleys, onepulley being an expansible pulley comprising a pair of cones, andreleasable first fluid-pressure-operated means for moving said conestoward each other to increase the effective diameter of the expansiblepulley; the combination therewith of a movable support carrying one ofsaid shafts, second fluid-pressure-operated means for applying pressureto said support in a direction away from the other shaft, means toincrease the pressure in said second iluid-pressure-operated means whenpressure is released from said first fiuid-pressure-operated means sothe belt is maintained taut as the effective diameter of the expansiblepulley is decreased, and said last-named means being operable todecrease the pressure in said second fiuid-pressure-operated means whenthe effective diameter of said eXpansible pulley is increased to permitthe belt to pull the support toward said other shaft Without the belthaving to overcome the full force of the previously increased pressurein said second fluid-pressure-operated means.

15. In a variable speed drive for a spinning machine and the like havinga pair of spaced substantially parallel shafts, one shaft being driven,a pulley on each shaft, an endless belt entrained over said pulleys, onepulley being an expansible pulley comprising a pair of cones, firstliuid-pressure-operated means for moving said cones toward each other toincrease the eifective diameter of the expansible pulley, and means toincrease and decrease the pressure in said first fiuid-pressure-operatedmeans; the combination therewith of a movable support carrying one ofsaid shafts, second fiuid-pressure-operated means for applying pressureto said support in a direction away from the other shaft, means toproportionally increase the pressure in said secondfluid-pressure-operated means when pressure is decreased in said firstfiuid-pressure-operated means so the belt is maintained taut as theeffective diameter of the expansible pulley is decreased, and saidlast-named means being operable to proportionally decrease the pressurein said second fiuid-pressure-operated means when the pressure isincreased in said first fluidpressure-operated means and the effectivediameter of said expansible pulley is increased so the belt pulls thesupport toward said other shaft without the belt being encumbered byexcessive pressure in said second fluidpressure-operated means.

16. A structure according to claim 15, in which said means to increaseand decrease pressure in said first fluid-pressure-operated meanscomprises a first pressure iii regulator valve and said means toincrease and decrease pressure in said second fluid-pressure-operatedmeans comprises a second pressure regulator valve, and means to open andclose either valve in unison with the respective closing and opening ofthe other valve.

17. in a structure according to claim 16, said machine having avertically reciprocating ring rail, and said lastnanied means beingautomatically operable to open one valve and close the other valve at apredetermined instant before initiation of each movement of said rail inone direction, and to close said one valve and open the other valve at apredetermined instant before initiation of each movement of said ringrail in the opposite direction.

18. A structure according to claim 16 wherein said machine includes avertically reciprocating ring rail, said means to open and close eithervalve being automatically operable to initiate the opening of one valveand the closing of the other valve at a predetermined instant precedinginitiation of movement of said ring rail in one direction and tocontinue gradual opening of said one valve and gradual closing of theother valve during subsequent movement of said ring rail in said onedirection, and said means to open and close either valve also beingautomatically operable to initiate the closing of said one valve and theopening of said other valve at a predetermined instant precedingmovement of said rail in the other direction and to continue gradualclosing of said one valve and gradual opening of said other valve duringsubsequent movement of said rail in said other direction.

19. In a variable speed drive for a spinning machine and the like havinga rotating builder motion cam, a pair of spaced substantially parallelshafts, one shaft being driven, a pulley on each shaft, an endless beltentrained over said pulleys, one pulley being an expansible pulleycomprising a pair of cones, first fluid-pressure-operated means formoving said cones toward each other to increase the effective diameterof the expansible pulley, and means under control of said cam forgradually increasing and decreasing the pressure in said firstfluidpressure-operated means in alternation; the combination therewithof a movable support carrying one of said shafts, secondiluid-pressure-operated means for applying pressure to said support in adirection away from the other shaft, means to gradually increase thepressure in said second fluid-pressure-operated means in inverserelation to the gradual decrease in pressure in said firstfiuid-pressure-operated means so the belt is maintained taut and spreadsapart said cones and the eifective diameter of the expansible pulley isthereby decreased, and said last-named means being operable to graduallydecrease the pressure in said second fiuid-pressure-operated means ininverse relation to the gradual increase in pressure in said firstfluid-pressure-operated means and when the effective diameter of saidexpansible pulley is increased so the belt pulls the support toward saidother shaft without the belt being encumbered by excessive pressure insaid second fluid-pressure-operated means.

20. A structure according to claim 19 wherein said machine is providedwith a vertically reciprocable ring rail operatively connected with saidbuilder motion cam; said means under control of said cam for graduallyincreasing and decreasing the pressure in said firstfluid-pressureoperated means comprising a pivoted follower arm, a camfollower longitudinally adjustable on said arm and engaging said carn, afirst pressure regulator valve interposed in a fluid pressure system tosaid first fiuid-pressure-operated means, said means to graduallyincrease and de crease the pressure in said secondfiuid-pressure-operated means comprising a second pressure regulatorvalve interposed in a fluid pressure system to said secondfluidpressure-operated means, each valve having a plunger normallybiased to closed position, a pivoted actuating lever adapted to open oneof said valves while substantially releasing the plunger on the other ofsaid valves with movement thereof in one direction and being adapted tosubstantially release the plunger of said one of said valves and to openthe other of said valves with movement thereof in the other direction,and means operatively connecting said follower arm with said leverWhereby movement of said follower arm in opposite directions impartsrespective movements to said lever.

21. A structure according to claim 20 including an intermediate pivotedlever having opposed portions engaging said valve plungers, andadjustable means spaced from opposite sides of the pivot point of saidactuating lever and being engageable with said intermediate lever forimparting movement thereto and to the respective plungers.

22. In a machine having spindles and at least one ring rail, saidmachine also having means for rotating said spindles and continuouslyreciprocating said rail; the combination therewith of regulating meansfor producing a gradual increase in the speed of the spindles and thering rail during movement of the ring rail in one direction and forproducing a gradual decrease in the speed thereof with movement of thering rail in the opposite direction, controlling means operativelyassociated with said regulating means for controlling the rate, rangeand extent of the variation in speed of the spindles and rail, meansautomatically operable for initiating said gradual increase in speed ata predetermined relatively short interval preceding initiation ofmovement of said ring rail in said one direction, said automaticallyoperable means also being operable a predetermined interval precedinginitiation of movement of said rail in said opposite direction toinitiate said gradual decrease in speed, and means for adjusting saidautomatically operable means independently of said controlling meanswhereby the instants at Which the gradual changes in speed are reversedmay be determined independently of the rate, range and extent of speedvariation effected by said regulating means and independently of thelocation of the ring rail.

References Cited in the file of this patent UNITED STATES PATENTS2,507,904 Heller et al. May 16, 1950 2,803,107 Long Aug. 20, 19572,901,883 Granberry Sept. 1, 1959

